DE102014103958A1 - Motor-pump unit - Google Patents

Abstract

The invention relates to a motor-pump unit (20) with an electric motor (22) and a reversible internal gear machine (21). The latter has a multipart housing (25) in which an externally toothed pinion (26) and an internally toothed ring gear (30) are arranged. Between the gears (26, 30) is a free space formed in which a multipart filler is arranged. The filler comprises a plurality of radially movable radial sealing segments, between which a radial gap is formed. Between axial Stirnfächen the gears (26, 30) and a housing part (25.1, 25.2) of the housing (25) an axially movable Axialdichtplatte (58.2) is arranged. This has a to the end faces of the gears (26, 30) towards open, acted upon by pressure medium sealing plate-control groove, which is open to the radial gap and this is directly opposite. The pinion segment and / or the Hohlradsegment have a pressurizable means, transversely extending Radialdichtsegment control channel, which is open to the radial gap and opens directly into the radial gap.

Description

The invention relates to a motor-pump unit comprising an internal gear machine for reversing operation and an electric motor which is coupled via a shaft with the internal gear machine. Preferably, optionally or depending on the direction of rotation, the internal gear machine can be driven or driven by means of the electric motor as an internal gear pump or the electric motor can be driven or driven by means of the internal gear machine as a power generator. Such a motor-pump unit can be used for example to control a highly dynamic hydraulic axis.

In such motor-pump units, it depends on a high dynamics, low noise and Pulsationsarmut, Rekupierbarkeit, long life, freedom from leaks, long life and insensitivity to shock, dirt, water, especially salt water and temperature, especially cold on.

In the hitherto known motor-pump units, it can come in high-dynamic reversing at the respective reversal of direction to a slump in the promotion of the pressure medium and thus to a strong inconsistency of the pressure medium flow rate.

It is an object of the invention to avoid these disadvantages. This object is solved by the features of claim 1.

According to a further development, it can be provided that the pinion segment and / or the ring gear segment has a sealing roller groove extending in the axial direction, in which a sealing roller movable in the radial direction relative to the pinion segment and to the ring gear segment for sealing the radial gap between the pinion gear segment and the ring gear segment is arranged and that the pinion segment and / or the ring gear segment has a extending in the axial direction segment spring groove which is arranged offset in a circumferential distance to the sealing roller groove in the direction of the high-pressure region associated pinion segment end of the pinion segment or Hohlradsegmentendes the Hohlradsegments, wherein in the segment spring groove a prestressed Is arranged spring, by means of which the Hohlradsegment and the pinion segment are pressed away from each other in such a radial direction that the pinion segment with a radially inwardly facing outer surface of pinion teeth of the Ritzelz rne of the pinion rests and that the Hohlradsegment with a radially outwardly facing outer surface facing away from the outer surface of the pinion segment, against Hohlradzähnen the Hohlradzähe of the ring gear and / or that the pinion segment is formed as a segment carrier for the ring gear segment and a stop with a In the axial direction and radially outwardly to the ring gear extending stop surface for supporting the ring gear against retraction during operation of the internal gear machine in the tooth engagement region, wherein the stop with its stop surface in a circumferential distance to the segment spring groove in the direction of the high pressure region associated pinion end of the Sprocket segment is arranged offset or that the ring gear segment is designed as a segment carrier for the pinion segment and a stop with a in the axial direction and radially inwardly toward the pinion extending axial stop surface to Supporting the pinion segment against retraction during operation of the internal gear machine in the tooth engagement region, wherein the stop is arranged offset with its stop surface at a circumferential distance to the segment spring groove in the direction of the high pressure region associated ring gear segment end of the ring gear segment.

According to an advantageous development can be provided that the sealing plate control channel is formed as a sealing plate-control groove.

According to a particularly advantageous embodiment variant, it can be provided that the sealing plate control channel has a V-shaped cross section in a cross section running parallel to the axial direction.

It may be particularly advantageous if the sealing plate control channel extends along the radial slot and / or if the sealing plate control channel extends in the circumferential direction.

According to a particularly preferred embodiment, it can be provided that the sealing plate control channel has a control channel length, via which it is open to the radial slot and the radial slot is directly opposite over its entire control channel length.

According to a very particularly preferred embodiment, it may be provided that the sealing plate control channel opens into an essentially pressure-sensitive, preferably kidney-shaped, sealing plate recess, in particular a sealing kidney, of the axial sealing plate, which is assigned to the same sides of the toothed wheels axial faces of the gears is open and this is directly opposite, so that the sealing plate control channel via the sealing plate recess can be acted upon directly with the pressure medium. The sealing plate Recess may also be referred to as a sealing plate control recess.

Particularly preferably, it can be provided that the sealing plate control channel extends from the sealing plate recess, preferably in the circumferential direction, along the radial slot.

According to a particularly preferred embodiment, it can be provided that the sealing plate control channel extends from the sealing plate recess, preferably in the circumferential direction, either along the radial slot into a region which lies directly opposite the segment spring groove or along the radial slot and the segment spring groove, the segment spring groove immediately opposite, extends into a region which is arranged either between the segment spring groove and the sealing roller groove or which extends to the sealing roller groove or which is directly opposite the sealing roller groove.

According to a particularly preferred embodiment it can be provided that the Radialdichtsegment control channel extends in a direction or circumferential direction in which the pinion about its pinion axis or in which the ring gear is rotatable about its Hohlraddrehachse and / or that the Radialdichtsegment Control channel extends in a transverse or perpendicular to the axial direction extending imaginary plane or circumferential direction.

According to a preferred embodiment, it is provided that the radial sealing segment control channel is designed as a chamfer or a groove or that at least a first radial sealing segment control channel is designed as a chamfer and at least a second radial sealing segment control channel are designed as a groove.

According to a particularly advantageous embodiment, it can be provided that the radial sealing segment control channel extends between the segment spring groove and the sealing roller groove and / or that the radial sealing segment control channel opens into the segment spring groove and / or into the sealing roller groove and / or that the radial sealing segment control channel between the segment spring groove and the abutment surface of the stop extend and / or that the Radialdichtsegment control channel extends to the stop surface of the stop and / or that the Radialdichtsegment control channel over or beyond the stop surface of the stop out to a ring gear teeth of the ring gear teeth of the ring gear opposite free surface of the pinion gear segment and / or the ring gear segment extends.

According to a preferred development it can be provided that the pinion segment and / or the ring gear segment or the filler is or are formed sickle-shaped.

According to an advantageous development, the pinion segment can be designed in one piece and / or be made of one part and / or the ring gear segment can be designed in one piece and / or be made of one part.

According to a preferred embodiment it can be provided that the radial sealing segments comprise at least two or exactly two ring gear segments and / or that the radial sealing segments comprise at least two or exactly two pinion segments.

According to a particularly preferred embodiment it can be provided that the pinion segment and / or the Hohlradsegment by means of at least one retaining pin which is rotatably mounted in a the same sides of the gears associated axial end faces of the gears opposite housing part of the housing, against a displacement in the direction of Low pressure region or a suction side of the working chamber is mounted, wherein the retaining pin has at its end associated with the filling piece a holding body, which, viewed in a cross section perpendicular to the axial direction, a V-shaped or trapezoidal cross-section and comprises holding body support surfaces, the one include tips, preferably 20 to 30 degrees or amounts to approximately 24 degrees, angle, and wherein the pinion segment and / or the ring gear segment has at least one sealing segment recess for receiving the holding body of the at least one retaining pin, in a em cross-section viewed perpendicular to the axial direction, also has a V-shaped or a trapezoidal cross-section and sealing segment support surfaces, which also include an acute, preferably 20 to 30 degrees or amounts to about 24 degrees angle, and wherein both the holding body Support surfaces and the sealing segment support surfaces extend in a wedge shape towards a center toward the pinion, and wherein the at least one retaining pin engages with its holding body in the at least one sealing segment recess.

According to a preferred embodiment, at least two Axialdruckfelder may be provided in the form of recesses or depressions, which are provided in the at least one Axialdichtplatte and / or which are provided in the housing part, the at least one Axialdichtplatte on its away from the gears away side opposite lies. According to a likewise preferred embodiment, it can be provided that the at least one axial sealing plate has at least two control fields or pressure kidneys in the form of recesses or depressions on its side pointing toward the end faces of the toothed wheels.

According to a very particularly preferred embodiment it can be provided that the filler and / or the control panels or pressure kidneys of one or each Axialdichtplatte and / or the Axialdruckfelder and / or the at least one or each Axialdichtplatte symmetrical to an imaginary the pinion rotation axis and the ring gear Rotational axis containing symmetry plane is designed or are.

According to a particularly advantageous embodiment, it can be provided that the electric motor is a brushless DC motor (EC motor).

According to a particularly preferred embodiment, it can be provided that the shaft is a one-piece and / or one-piece motor pump shaft, to which the rotor is secured against rotation, preferably non-positively, in particular by pressing or shrinking, and on which the pinion rotatably, preferably form-fitting, in particular releasably secured.

It is understood that the above features and measures may be combined as desired within the scope of the invention.

Further features, advantages and aspects of the invention will become apparent from the claims and the drawings and from the following description part, in which a preferred embodiment of the invention with reference to figures.

Show it:

1 A perspective view of a motor-pump unit according to the invention;

2 a longitudinal section of a portion of the motor-pump unit in the region of the internal gear machine in a sectional plane containing the pinion rotation axis of the pinion and the ring gear rotation axis of the ring gear;

3 a cross section of the internal gear machine of the motor-pump unit along the section lines 3-3 in 2 ;

4 a perspective view of an axial sealing plate of the internal gear machine;

5 a plan view of the axial sealing plate according to 4 , wherein in dotted lines, the machine elements according to the view 3 are drawn to illustrate the position and arrangement of the elements to each other;

6 a perspective view of the filler forming and supporting components, in an exploded view;

7 a plan view of the Axialdichtplatte on its side facing away from the teeth side opposite housing part of the housing of the internal gear machine;

8th a perspective view of an arrangement of a sealing ring and a support ring for the sealing ring in an exploded view;

9 a perspective view of an arrangement in which the support ring and the sealing ring are assembled in a mounted position;

10 an enlarged section of a cross section of the arrangement according to 9 along the lines 10-10;

11 a longitudinal section of the motor-pump unit in a sectional plane containing the pinion rotation axis of the pinion and the ring gear rotation axis of the ring gear;

12 a longitudinal section of the motor-pump unit in a sectional plane according to the section lines 12-12 in 11 ;

13 a greatly enlarged section according to the in 12 marked circle;

14 a cross section of the motor-pump unit in a sectional plane according to the section lines 14-14 in 11 ;

15 a greatly enlarged section according to the in 14 marked subcircle.

The motor-pump unit 20 includes an internal gear machine 21 for reversing operation, an electric motor 22 and integrated electronics 74 in particular for speed control. The electric motor 22 includes a rotor 22.1 and a stator 22.2 , The relative to the stator 22.2 around a rotor axis of rotation 34.1 rotatable rotor 22.1 is non-rotatable with one around a shaft rotation axis 35 rotatable shaft 23 connected. The rotor 22.1 is about the wave 23 with the gear of the internal gear machine 21 coupled. Preferably, the shaft is 23 around a common one-piece motor pump shaft. The motor pump shaft 23 is about a shaft rotation axis 35 rotatably in the housing 25 stored. The motor-pump unit 20 can be preferably used for the control of a highly dynamic hydraulic axis, which or are not shown in the figures.

The motor-pump unit 20 includes a multi-part housing 25 that is both the electric motor 22 as well as the internal gear machine 10 contains. In the embodiment shown, both the rotor 22.1 as well as the stator 22.2 in a motor 22 associated tubular housing part 25.3 of the housing 25 arranged. However, it is understood that the stator could also form part of a housing part of the housing of the motor-pump unit or could be formed as a housing part of the housing of the motor-pump unit. In the internal gear machine 21 It is a hydraulic machine in the form of a compensated four-quadrant internal gear machine 21 , Preferably, the motor-pump unit 20 used in a closed hydraulic system. The motor-pump unit 20 is characterized by high dynamics, low noise and Pulsationsarmut, Rekupierbarkeit, a long life, absolute freedom from leaks, lifetime filling of the system, shock resistance and insensitivity to dirt, water, especially salt water, and temperature, especially cold from. This is indicated by the motor-pump unit 20 especially the following design features:

Internal gear pump:

As internal gear machine 21 A hydraulic pump in the form of an internal gear pump with axial and radial sealing gap compensation is used. The internal gear machine 21 includes a working chamber 24 that of preferably two housing parts 25.1 and 25.2 of the housing 25 the motor-pump unit 20 is limited. In the case 25 or in the working chamber 24 are two gears 26 . 30 arranged. It is a pinion teeth 28 having externally toothed pinion 26 and a ring gear teeth 31 having internally toothed ring gear 30 , The ring gear 30 is with respect to the pinion 26 eccentric in a bearing ring 27 stored. The bearing ring 27 is non-rotatable with the housing part 25.2 of the housing 25 connected, preferably pressed. The ring gear 30 is arranged such that ring gear teeth of the ring gear teeth 31 of the ring gear 30 in a meshing area 33 with pinion teeth of the pinion teeth 28 of the pinion 26 comb. The pinion 26 is about a pinion axis of rotation 34.2 rotatably mounted. The pinion axis 34.2 is coaxial with the shaft rotation axis 35 the wave 23 arranged. The ring gear 30 is about a Hohlraddrehachse 36 rotatably mounted. The directions of rotation of pinion 26 and ring gear 30 are rectified. This means that when, for example, the pinion 26 turns clockwise, then forcibly also the ring gear 30 turns clockwise. Preferably, the pinion 26 with the wave 23 releasably connected, for example via a feather key 37 that fit into grooves 38.1 . 38.2 both the wave 23 as well as the pinion 26 positively engages (see 3 ). Consequently, the pinion 26 and the wave 23 positively connected rotationally fixed to each other. The ring gear axis of rotation 36 and the pinion rotation axis 34.2 extend in an axial direction 39 parallel to each other.

Between the pinion 26 and the ring gear 30 is a crescent-shaped space 40 the working chamber 24 educated. In the open space 40 is a multi-part crescent-shaped filler 41 arranged. The filler 41 comprises a plurality of radial sealing segments movable relative to one another in the radial direction 42 ; 43.1 . 43.2 for the radial sealing of each of the direction of rotation 104.1 . 104.2 dependent "active" high-pressure range 44.1 . 44.2 the working chamber 24 , The high pressure area 44.1 . 44.2 is the area of the working chamber 24 associated, starting from a pressure build-up area of the working chamber 24 in the operation of the internal gear machine 21 approximately corresponds to the area in which the teeth 28 . 31 the gears 26 . 30 the filler 41 or the area of the filler 41 reach, in which at least one, preferably two, retaining pin / e or retaining bolts 45.1 . 45.2 for the filler 41 or for its radial sealing segments 42 ; 43.1 . 43.2 is arranged, in the respective direction of rotation 104.1 . 104.2 from pinion 26 or ring gear 30 considered, up to the meshing area 33 extends in which the teeth 28 . 31 the gears 26 . 30 comb each other. The respective active high pressure area 44.1 . 44.2 is semi-sickle-shaped or kidney-shaped. When the internal gear pump 21 rotates in its first operating direction, in which the pinion 26 and the ring gear 30 in their first direction of rotation 104.1 rotate, fluid high pressure forms in a first area 44.1 the working chamber 24 which is then the active first high pressure area 44.1 is. In contrast, then forms in the second area 44.2 the working chamber from a fluid low pressure. When the internal gear pump 21 rotates in its second operating direction opposite to the first operating direction, in which therefore the pinion 26 and the ring gear 30 in its second direction of rotation 104.2 opposite to the first direction of rotation 104.1 rotate, fluid high pressure forms in the second area 44.2 the working chamber 24 which is then the active second high pressure area 44.2 is. In contrast, then forms in the first area 44.1 the working chamber from a fluid low pressure. In the said first area 44.1 the working chamber 24 opens a first connection channel 105.1 and in the said second area 44.2 the working chamber opens a second connection channel 105.2 , (please refer 12 ). So if the internal gear pump 21 in their first operating direction 104.1 turns, is or becomes the first working channel 105.1 subjected to fluid high pressure and when the internal gear pump 21 in their second operating direction 104.2 turns, is or becomes the second working channel 105.2 subjected to fluid high pressure of the fluid pressure medium. Preferably, the first connection channel extend 105.2 and the second connection channel 105 , in the axial direction 39 parallel to each other

The radial sealing segments 42 ; 43.1 . 43.2 include a first radial sealing segment, which can be a markable as a segment carrier pinion segment 42 forms, the pinion teeth of the pinion teeth 28 of the pinion 26 can be applied or applied. The pinion segment 42 is formed in one piece and made of one part, for example by milling.

The radial sealing segments 42 ; 43.1 . 43.2 In addition, at least one second Radialdichtsegement that a ring gear segment 43.1 . 43.2 forms and that at Hohlradzähnen the Hohlradzähne 31 of the ring gear 30 can be applied or applied. In the preferred embodiment shown in the figures, there are two separate ring gear segments 43.1 . 43.2 provided, each of which ring gear segment 43.1 . 43.2 at Hohlradzähnen the Hohlradzähne 31 of the ring gear 30 can be applied or applied. The pinion segment 42 points in each case in the region of each ring gear segment 43.1 . 43.2 a radially outward to the respective Hohlradsegment 43.1 . 43.2 facing inner surface 72 on. Each ring gear segment 43.1 . 43.2 has a radially inward to the pinion segment 42 facing inner surface 73.1 . 73.2 on which of the associated inner surface 72 of the pinion segment 42 is opposite. Between the inner surface 72 of the pinion segment 42 and the inner surface 73.1 . 73.2 of the respective ring gear segment 43.1 . 43.2 each is a radial gap 75.1 . 75.2 educated. In operation of the internal gear machine 21 passes pressure medium, preferably pressure oil, from the current direction of rotation of the pinion 26 and the ring gear 30 associated active high pressure area 44.1 . 44.2 in the said radial gap 75.1 . 75.2 or in the corresponding gap space, which is also designated compensation space. This will - depending on the direction of rotation of pinion 26 and ring gear 30 - One of the two Hohlradsegmente 43.1 . 43.2 , namely the current or active high-pressure chamber 44.1 . 44.2 assigned ring gear segment 43.1 . 43.2 , which is then denoted as active Hohlradsegment, and the pinion segment 42 away from each other or pushed apart, so that the pinion segment 42 with an outer surface 46 on tooth tips of pinion teeth of the pinion teeth 28 of the pinion 26 is pressed sealingly and also the active ring gear segment 43.1 . 43.2 with an outer surface 47.1 . 47.2 on tooth tips of Hohlradzähnen the Hohlradzähne 31 of the ring gear 30 is pressed sealingly, so that said radial gap 75.1 . 75.2 is radially compensated in this way. In this context, one speaks of radial compensation or of a radially compensated internal gear machine 21 ,

In the embodiment shown, the pinion segment 43.1 . 43.2 two in the axial direction 39 extending sealing grooves 48.1 . 48.2 on. Every sealing groove 48.1 . 48.2 is open to their axial ends facing away from each other. In every sealing groove 48.1 . 48.2 is a radial direction relative to the pinion segment 42 and the respective associated ring gear segment 43.1 . 43.2 movable sealing roll 49.1 . 49.2 for sealing the radial gap 75.1 . 75.2 between the Ritzelsgement 42 and the respective ring gear segment 43.1 . 43.2 arranged. In every sealing groove 48.1 . 48.2 is also a preloaded sealing roll spring 50.1 . 50.2 , preferably a leaf spring arranged. Each seal roll spring 50.1 . 50.2 supported on the one hand on a groove bottom of the associated sealing roller groove 48.1 . 48.2 on the other hand, based on the associated sealing roller 49.1 . 49.2 from. This will make every sealing roll 49.1 . 49.2 also in the pressure-free state or in non-operation of the internal gear machine 21 against a sealing surface of the sealing roller groove 48.1 . 48.2 of the pinion segment 42 and also against a sealing surface of the respective associated Hohlradsegments 43.1 . 43.2 pressed.

Furthermore, the pinion segment 42 two in the axial direction 39 extending segment spring grooves 51.1 . 51.2 on. Each segment spring groove 51.1 . 51.2 is open to their axial ends facing away from each other. In every segment spring groove 51.1 . 51.2 is a preloaded spring 52.2 . 52.2 , preferably a leaf spring, added. Each segment spring groove 51.1 . 51.2 is at a circumferential distance or circumferential angle to the respectively associated sealing roller groove 48.1 . 48.2 offset in the circumferential direction, in the direction of the, depending on the direction of rotation, high pressure area 44.1 . 44.2 , associated pinion segment end 53.1 . 53.2 of the pinion segment 42 added. By means of this spring 52.1 . 52.2 become the associated ring gear segment 43.1 . 43.2 and the pinion segment 42 such in the radial direction away from each other or pushed apart that the pinion segment 42 with a radially inwardly facing outer surface 46 at Hohlradzähnen the Hohlradzähne 31 of the ring gear 30 sealingly abuts and that the ring gear segment 43.1 . 43.2 with a radially outwardly facing outer surface 47.1 . 47.2 that from the outside surface 46 of the pinion segment 42 points away, at Hohlradzähnen the Hohlradzähe 31 of the ring gear 30 sealingly applied.

The pinion segment 42 is as a segment carrier for the respective ring gear segment 43.1 . 43.2 designed and has for each Hohlradsegment 43.1 . 43.2 a markable as a billboard stop 54.1 . 54.2 on. Everyone 54.1 . 54.2 Stop has one in the axial direction 39 and radially outward to the ring gear 30 towards extending stop surface 55.1 . 55.2 for supporting the respective ring gear segment 43.1 . 43.2 against a retraction of the respective Hohlradsegments 43.1 . 43.2 during operation of the internal gear machine 21 in the meshing area 33 on. Every stop 54.1 . 54.2 is with its stop surface 55.1 . 55.2 in a circumferential distance or in a circumferential angle to the respective segment spring groove 51.1 . 51.2 in the circumferential direction in the direction of the dependent on the direction of rotation active high pressure area 44.1 . 44.2 associated pinion segment end 53.1 . 53.2 of the pinion segment 42 staggered.

For axial gap compensation of the respective axial gap between the respective sides of the gears pointing in the same direction 26 . 30 associated end faces 56.1 . 56.2 ; 57.1 . 57.2 the gears 26 . 30 and the respective housing part 25.1 . 25.2 are in the embodiment shown two in the axial direction 39 movable axial sealing plates 58.1 . 58.2 intended. These serve to seal off the direction of rotation of the gears 26 . 30 dependent high-pressure range 44.1 . 44.2 the working chamber 24 to effect. The axial sealing plates 58.1 . 58.2 can also be called axial discs. It is understood that even a single Axialdichtscheibe can be provided. The or each Axialdichtscheibe 58.1 . 58.2 is between each associated end faces 56.1 . 56.2 ; 57.1 . 57.2 the gears 26 . 30 and a housing part 25.1 . 25.2 of the housing 25 arranged.

The or each axial sealing disc 58.1 . 58.2 becomes in operation of the internal gear machine 21 by means of pressure medium under high pressure with their respective inner surface 59.1 . 60.1 against the respective associated end faces 56.1 . 56.2 ; 57.1 . 57.2 from pinion 26 and ring gear 30 pressed. For this purpose, so-called pressure fields 61.1 . 61.2 provided, which are also marked with Axialfelder (see 7 ). The pressure fields 61.1 . 61.2 form tax fields. The pressure fields 61.1 . 61.2 are in this embodiment in the form of recesses in the respectively associated housing part 25.1 . 25.2 of the housing 25 intended. However, it goes without saying that the pressure fields or a pressure field associated with an axial sealing plate can also be provided in the form of a recess in the axial sealing plate or in the respective axial sealing plate. The or each pressure field 61.1 . 61.2 is kidney-shaped.

The axial discs 58.1 . 58.2 show on their insides 59.1 . 60.1 So those pages, which the pinion 26 and the ring gear 30 facing, kidney-shaped control panels 62.1 . 62.2 on, which are also referred to as sealing plate recesses or Drucknieren (see 4 and 5 ).

These are recesses or depressions in the respective axial disc 58.1 . 58.2 , These panels 62.1 . 62.2 are, as well as the pressure fields 61.1 . 61.2 , be acted upon with pressure medium under high pressure or be during operation of the internal gear machine 21 with pressure medium of the respective high pressure area 44.1 . 44.2 applied. As a result, a counter force is generated, which the force of the pressure fields 61.1 . 61.2 counteracts. Every print kidney 62.1 . 62.2 are at least two pilot grooves 63.1.1 . 63.1.2 ; 63.2.1 . 63.2.2 assigned to each of the associated end faces 56.1 . 56.2 ; 57.1 . 57.2 the gears 26 . 30 are open, of which a first Steuerut 63.1.1 . 63.1.2 in the area of between the pinion teeth 28 of the pinion 26 trained sprocket tooth spaces 29 this is arranged directly opposite and of which a second control groove 63.2.1 . 63.2.2 in the region of between the ring gear teeth 31 of the ring gear 30 trained ring gear tooth gaps 32 this is arranged directly opposite (see 5 ). Both the first tax good 63.1.1 . 63.1.2 as well as the second control groove 63.2.1 . 63.2.2 each lead with a first end in the associated print kidney 62.1 . 62.2 , At a respective second end of the first and second control groove 63.1.1 . 63.1.2 ; 63.2.1 . 63.2.2 each facing away from the first end in the circumferential direction is a control slot, respectively 64.1.1 . 64.1.2 ; 62.2.1 . 64.2.2 in the form of a recess or depression of the respective axial disc 58.1 . 58.2 intended. Every control slot 64.1.1 . 64.1.2 ; 62.2.1 . 64.2.2 opens into the respectively assigned first and second control groove 63.1.1 . 63.1.2 ; 63.2.1 . 63.2.2 , Every control slot 64.1.1 . 64.1.2 ; 62.2.1 . 64.2.2 extends approximately or substantially in the circumferential direction.

In addition to the above features, the motor-pump unit according to the invention 20 or the internal gear machine according to the invention 21 Inter alia, the following features essential to the invention:
The at least one axial sealing plate 58.1 . 58.2 points to her to the faces 56.1 . 56.2 ; 57.1 . 57.2 the gears 26 . 30 indicative side or inside 59.1 . 60.1 at least one of the faces 56.1 . 56.2 ; 57.1 . 57.2 the gears 26 . 30 towards open sealing plate recess or recess 63.3.1 . 63.3.2 in the form of an acted upon by pressure additional or third sealing plate control channel, which is designed as a sealing plate control groove. This is in the preferred embodiment shown, a third control channel of three control channels, which in each case in the pressure medium can be acted upon kidney-shaped sealing plate recess or Druckniere 62.1 . 62.2 of the both sealing plate recesses or pressure kidneys 62.1 . 62.2 each axial disc 58.1 . 58.2 empties. The said additional or third sealing plate control channel 63.3.1 . 63.3.2 is to the associated radial gap 75.1 . 75.2 towards open and lies the associated radial gap 75.1 . 75.2 directly opposite (see 5 ). The respective additional or third sealing plate control channel 63.3.1 . 63.3.2 extends from the respective sealing plate recess or pressure kidney 62.1 . 62.2 in the circumferential direction along the associated radial gap 75.1 . 75.2 between the pinion segment 42 and the associated ring gear segment 43.1 . 43.2 into a region which the segment spring groove 51.1 . 51.2 immediately opposite. The said additional sealing plate control channel 63.3.1 . 63.3.2 has in contrast to the respective first and second control groove 63.1.1 . 63.1.2 ; 63.2.1 . 63.2.2 no control slot on. Through the respective additional sealing plate control channel or through the respective third control groove 63.3.1 . 63.3.2 is achieved that the necessary radial compensation pressure in the associated radial gap 75.1 . 75.2 between the pinion segment 42 and the respective active ring gear segment 43.1 . 43.2 is reached almost simultaneously with the respective direction of rotation reversal and thus each a particularly advantageous seal.

In the internal gear machine 21 is additionally provided according to the invention that the pinion segment 42 and / or the ring gear segment 43.1 . 43.2 at least one radial-sealing-segment recess in the form of a groove in a circumferential direction about the pinion axis of rotation 34.2 or around the Hohlraddrehachse 36 extending, acted upon by the pressure medium Radialdichtsegment control channel 65 ; 65.1 . 65.2 . 65.3 . 65.4 . 65.5 . 65.6 having, to the associated radial gap 75.1 . 75.2 is open and directly into the associated radial gap 75.1 . 75.2 empties. Preferably, the radial sealing segment control passage extends 65 in one direction or in the direction of rotation in which the pinion 26 around its pinion axis 34.2 or in the ring gear 30 about its Hohlraddrehachse ( 36 ) is rotatable and / or and / or extends the Radialdichtsegment control channel 65 in a direction perpendicular to the axial direction 39 extending imaginary plane lying direction. By the above measures may be in the active pressure chamber 44.1 . 44.2 constituting pressure medium, preferably pressure oil, faster into the gap of the active radial gap 75.1 . 75.2 reach. This will provide the necessary radial compensation pressure in the active radial gap 75.1 . 75.2 between the pinion segment 42 and the respective active ring gear segment 43.1 . 43.2 achieved in even shorter time at the respective direction of rotation reversal and thus in each case an even better or optimal seal.

Apart from the above features are in the internal gear machine according to the invention 21 provided further measures or features, which have been found to be particularly advantageous for the purpose mentioned above. This allows the to this motor pump unit 20 particular requirements are met:

gearing:

The demand for low noise and Pulsationsarmut is made by a specially designed involute toothing with 15 teeth 28 on the pinion 26 and 20 teeth 31 on the ring gear 30 reached. Although a higher number of teeth would result in a further reduction of the flow rate pulsation, but at the same time increase the ring gear diameter. This would mean more space and a reduction of the hydraulic-mechanical efficiency of the gear machine. In addition, the manufacturing costs would be increased. Apart from that, the mass moment of inertia of the gear pump would be increased due to the larger Hohlraddurchmessers. However, with high dynamic requirements of up to 10 changes of direction per second, a low mass moment of inertia is decisive for the energy efficiency of the motor-pump unit 20 ,

Both the externally toothed pinion as 26 also the internally toothed ring gear 30 are profile shifted. The pressure angle is 25 °. The tooth crown height factor of the pinion teeth is 1.25 and the tooth crown height factor of the ring gear teeth is 1.24. This combination has proven to be extremely quiet. The tooth tip edges are specially shaped.

By a low backlash (0.02 to 0.05 mm or 0.01 to 0.025 × module) is achieved that even with highly dynamic reversing operation only very little pressure medium, in particular pressure oil, can flow via the tooth engagement to the "suction side".

Radial compensation:

The radial compensation is by three, also referred to as Radialdichtsegmente, segment parts 42 ; 43.1 . 43.2 shown symmetrically. The one-piece sprocket segment 42 is actively sealing both directions of rotation in pump and motor operation. The two ring gear segments 43.1 . 43.2 are only actively sealing when the direction of rotation is appropriate. The non-active sealing segment 43.1 . 43.2 is by a spring element 52.1 . 52.2 kept in position. The seal between the radial sealing segments 42 ; 43.1 . 43.2 that is, between the pinion segment 42 and the respective ring gear segment 43.1 . 43.2 , is made by sealing rollers arranged on both sides 49.1 . 49.2 guaranteed. The sealing rolls 49.1 . 49.2 consist of a high-strength temperature-resistant plastic. The sealing rolls 49.1 . 49.2 are in suitable recesses 48.1 . 48.2 of the pinion segment 42 added. The sealing rolls 49.1 . 49.2 become in operation of the internal gear machine 21 under pressure medium pressure against a sealing surface of the pinion segment 42 and against a sealing surface of the respective active ring gear segment 43.1 . 43.2 pressed. In the depressurized state, the sealing rollers 49.1 . 49.2 through the respective sealing roll spring 50.1 . 50.2 pressed against the sealing surfaces. The sealing surfaces are in a special angle 66 arranged smaller than 110 °. This is due to the contact pressure of the sealing rollers 49.1 . 49.2 also a radial "spread" of the radial sealing segments 42 ; 43.1 . 43.2 and thus a system of radial sealing segments 42 ; 43.1 . 43.2 to the teeth of the teeth 28 . 31 from pinion 26 and ring gear 30 reached.

The hydraulic control takes place via the radial gap 75.1 . 75.2 between the outer peripheral surface, also referred to as inner surface 43 of the pinion segment 42 and the respective inner circumferential surface, also referred to as inner surface 44.1 . 44.2 of the respective ring gear segment 43.1 . 43.2 , For safe control is in at least one Axialdichtplatte, preferably in the Axialdichtplatten 58.1 . 58.2 , at least one additional Steuerut 63.3.1 . 63.3.2 appropriate. By this at least one additional Steuerut 63.3.1 . 63.3.2 can the pressure medium or control oil not only on the radial gap 75.1 . 75.2 between the radial sealing segments 42 ; 43.1 . 43.2 get into the associated gap space, but also on the end faces or end face side in the gaps between the segments 42 ; 43.1 . 43.2 , This "double" control has proven to be extremely effective, especially in the dynamic requirements of reversing the internal gear machine 21 to get no break in the promotion. In other words, this creates the necessary radial compensation pressure in the gap 75.1 . 75.2 between the segments 42 ; 43.1 . 43.2 achieved almost "at the same time" with the reversal of direction and thus an optimal radial seal.

Further optimizations are by chamfering 65.1 . 65.2 . 65.5 . 65.6 and / or grooves 65.3 . 65.4 at the pinion segment 42 and / or on the ring gear segments 43.1 . 43.2 possible. The chamfers 65.1 . 65.2 . 65.5 . 65.6 can advantageously both sides, but also on one side of the segments 42 ; 43.1 . 43.2 be attached. Through these chamfers 65.1 . 65.2 . 65.5 . 65.6 can the building up in the pressure chamber pressure medium or pressure oil faster in the gap, ie in the radial gap 75.1 . 75.2 formed gap or compensation space between pinion 26 and active ring gear segment 43.1 . 43.2 to the respective sealing roller 49.1 . 49.2 reach. These chamfers 65.1 . 65.2 can, as shown, between the segment spring groove 51.1 and the sealing groove 48.1 and / or from the segment spring groove 51.1 up to the stop bag or until it stops 54.1 on the segment carrier 42 and / or over the entire stop surface 55.1 out to the open space 67.1 be arranged. About these chamfers 65.1 . 65.2 can then pressure medium or pressure oil directly or directly into the gap or compensation space 75.1 . 75.2 flow. Alternatively or additionally, as shown, these chamfers 65.5 . 65.6 at the ring gear segments 43.1 . 43.2 be attached. The same tasks can also tax people 65.3 . 65.4 on the outer circumference of the pinion segment 42 and / or on the inner circumference of the Hohlradsegmente take over.

In the embodiment shown, the filler is 41 over two retaining pins or bolts 45.1 . 45.2 supported by appropriate drilling 68.1 . 68.2 in the housing parts 25.1 . 25.2 are rotatably mounted. The retaining pins or bolts 45.1 . 45.2 have a Führungsläge a circular cylindrical guide area 69.1 . 69.2 on, which spans an outer diameter. Preferably, the guide length is 1.5 × outer diameter of the guide region 69.1 . 69.2 , For cost reasons, the retaining pins or bolts 45.1 . 45.2 made of sintered material, preferably made of sintered iron, with appropriate strength. The inner diameter of the holes 68.1 . 68.2 the housing parts 25.1 . 25.2 is a few microns larger than the outer diameter of the guide area 69.1 . 69.2 the retaining pins or bolts 45.1 . 45.2 , This results in a clearance fit. Thus, the retaining pins or bolts can 45.1 . 45.2 during operation of the internal gear machine 21 turn and the, preferably an angle 70 24 ° enclosing, contact surfaces 71.1 . 71.2 , can in one for the sealing function of the segments 42 ; 43.1 . 43.2 turn the optimal position. The fact that the guide length is 1.5 × outer diameter, on the one hand reduces the surface pressure and on the other hand, an impermissible tilting of the respective retaining pin or pin 45.1 . 45.2 in the receiving hole 68.1 . 68.2 of the respective housing part 25.1 . 25.2 avoided. A wear protection layer on the outer diameter of the respective retaining pin or bolt 45.1 . 45.2 increases the life of the gear machine 21 especially with highly dynamic load and change of direction as well as dynamic switching between motor and pump operation. For cost reasons, this wear protection is achieved by a surface hardening, such as nitriding or carbonitriding with appropriate choice of material.

The respective holding pin or bolt 45.1 . 45.2 has on its by the V-shaped arranged contact surfaces 71.1 . 71.2 pointing away side a circular cylindrical heel 76.1 . 76.2 , Of the paragraph 76.1 . 76.2 points opposite the management area 69.1 . 69.2 a much smaller outer diameter. The face 77.1 . 77.2 of the paragraph 76.1 . 76.2 is at the bottom of the bore hole in the housing part 25.1 . 25.2 and thereby forms an axial stop of the retaining pins or bolts 45.1 . 45.2 in the direction of the affected housing part 25.1 . 25.2 , In the direction of the radial sealing segments 42 ; 43.1 . 43.2 becomes the axial displaceability of the retaining pin or pin 45.1 . 45.2 through a frontal area 78.1 . 78.2 between the contact surfaces 71.1 . 71.2 and the groove bottom 79.1 . 79.1 the segment grooves 80.1 . 80.2 of the pinion segment 42 limited. The retaining pin or bolt 45.1 . 45.2 must always have an axial play, but may or may not with the teeth 28 . 31 of the pinion 26 or the ring gear 30 collide. For this purpose, open spaces are appropriate. The said paragraph 76.1 . 76.2 allows cost-effective production of the holes 68.1 . 68.2 in the housing parts 25.1 . 25.2 For example, by using a reamer with a relatively large chamfer bevel. This means that the bore 68.1 . 68.2 does not have to have the fit diameter to the bottom of the hole. To increase the fatigue strength of the retaining pin or pin 45.1 . 45.2 and thus the safety and durability of the hydraulic machine 21 , are at the transition of the contact surfaces 71.1 . 71.2 to the fit diameter as large as possible radii 81 appropriate. chamfers 82 on the segment-side end face 77.1 . 77.2 of the respective retaining pin or bolt 45.1 . 45.2 also allow at the groove bottom 79.1 . 79.2 for supporting on the retaining pin or bolt 45.1 . 45.2 certain grooves 80.1 . 80.2 of the pinion segment 42 radii 83 , These radii 81 . 83 reduce at the, preferably made of special brass or sintered, segments 42 ; 43.1 . 43.2 the notch stress, without affecting the mobility of the segments 42 ; 43.1 . 43.2 is limited by terminals.

The pressure build-up in the tooth spaces 29 . 32 from pinion 26 and ring gear 30 is through in the respective axial disc 58.1 . 58.2 introduced taxes 63.1.1 . 63.1.2 ; 63.2.1 . 62.2.2 and control slots 64.1.1 . 64.1.2 ; 64.2.1 . 64.2.2 controlled. These are in their position and the cross-sectional areas, in particular the control slots 64.1.1 . 64.1.2 ; 64.2.1 . 64.2.2 with a triangular V-shaped cross-section, preferably with a V-angle of 60 °, and an angle of inclination, preferably in the range of 4 °, optimized so that in interaction with the position and position of the segments 42 ; 43.1 . 43.2 , in particular the sealing roller position and the angle 70 the plant or support surfaces 71.1 . 71.2 ; 73.1 . 73.2 the retaining bolt 45.1 . 45.2 or the pinion segment grooves 80.1 . 80.2 as well as the position and position, in particular of the two side surfaces 84.1 . 84.2 the V-shaped open space 85 in the axial discs 58.1 . 58.2 , an optimal radial compensation effect of the pinion segment in almost all operating points 42 and the respective active ring gear segment 43.1 . 43.2 results. The tax people 63.1.1 . 63.1.2 ; 63.2.1 . 62.2.2 have a direct connection to the respective print kidney 62.1 . 62.2 the respective axial sealing disc 58.1 . 58.2 and thus become in operation of the internal gear machine 21 directly applied with pressure medium or with pressure oil. Preferably, control slots 64.1.1 . 64.1.2 ; 64.2.1 . 64.2.2 , Taxes 63.1.1 . 63.1.2 ; 63.2.1 . 62.2.2 ; 63.3.1 . 63.3.2 and printing kidneys 62.1 . 62.2 arranged on both sides of the transmission. But there are also one-sided solutions conceivable in which the cross sections are adjusted accordingly.

The retention of the segments 42 ; 43.1 . 43.2 is by the intervention of the respective retaining pin 45.1 . 45.2 into the corresponding grooves 80.1 . 80.2 in the pinion segment 42 and by a radial projection of the retaining pin 45.1 . 45.2 over the pinion segment 42 also reached radially outward. Thus, even in no-pressure operation, the position of the segments 42 ; 43.1 . 43.2 given in a positive fit. Thus the mobility or the displaceability with the segments 42 ; 43.1 . 43.2 in the previously described advantageous V-shaped configuration of the contact surfaces 71.1 . 71.2 of the retaining pin or bolt 45.1 . 45.2 is guaranteed, the grooves must 80.1 . 80.2 of the pinion segment 42 slightly larger or wider than that in the grooves 80.1 . 80.2 projecting, also called holding body part 86.1 . 86.2 of the respective retaining pin 45.1 . 45.2 , The clearance must match the gearbox tolerances of the body parts 25.1 . 25.2 , Segments 42 ; 43.1 . 43.2 , Bearing bushes and the deformation under load and taking into account the thermal expansion of the components in the temperature range of the application to be selected: It has proven advantageous to play between 0.05 to 0.1 × module of Verdrängerverzahnung. As a result, a jamming of the teeth by the wedge-shaped segments 42 ; 43.1 . 43.2 prevented even in depressurized operation.

axial compensation:

Like the radial compensation, the preferably double-sided axial compensation is also built up by autogenous pressure. The axial compensation is via axial pressure fields 61.1 . 61.2 controlled axial plates 58.1 . 58.2 symmetrical to one of the axes of rotation of pinion 26 and ring gear 30 containing symmetry plane 87 built up. This plane of symmetry 87 runs, in a direction perpendicular to the axial direction 39 or perpendicular to the axes of rotation 34.2 . 36 from pinion 26 and ring gear 30 extending cross section through the center 88 the axis of rotation 34.2 of the pinion 26 and through the center 89 the axis of rotation 36 of the ring gear 30 , This symmetry applies both to the respective axial disk 58.1 . 58.2 as well as for those in the preferably pot-shaped housing part 25.2 and / or in the preferably designed as a lid housing part 25.1 mounted axial pressure fields 61.1 . 61.2 ,

The sealing of the axial pressure fields 61.1 . 61.2 is preferably done by axial seals 90 with support rings 91 (please refer 8th to 10 ). In the case of axial seals without support rings, the axial seal would have to be completely or partially "chambered" in this highly dynamic, reversibly used hydraulic machine. This means that the groove for receiving the seal would also have to have an "edge" to the pressure field "inside". This necessary "edge" would complicate the production of the housing or lid parts. With support ring 91 can the pressure field 61.1 . 61.2 be made completely kidney-shaped. The bottom of the pressure fields 61.1 . 61.2 does not have to be completely machined, but can be made by casting, for example, die castings or other castings.

The support ring 91 also has the advantage that it has a gap extrusion of the axial seal 90 in the gap between axial plate 58.1 . 58.2 and housing or lid wall prevented. This allows the hydraulic machine 21 can also be used for higher pressures. A gap extrusion of the axial seal occurring without a support ring would also cause a slight increase in the active axial pressure field and thereby increase the compensation force. This in turn would lead to a reduction of the hydraulic-mechanical efficiency and would thus deteriorate the energy efficiency of the motor-pump unit. In the worst case, it could lead to failure of the hydraulic machine by seal failure or by increased wear of the running surfaces of the thrust washer to the transmission side.

The supporting action of the support rings 91 to "inside" is by one or more webs 92 significantly improved. The arrangement of these bars 92 must be chosen so that the oil flow is not affected in particular to the axial pressure output or the flow of oil from the inlet. In the example shown is the bridge 92 exactly at the same position as a bridge 93.1 . 93.2 who is in the pressure kidney 62.1 . 62.2 the respective axial disc 58.1 . 58.2 is arranged. The axial compensation is optimally matched in the example carried out by the measures described below. The symmetrical to the plane of symmetry 87 arranged pressure kidneys 62.1 . 62.2 whose limiting radii on the one hand project beyond the tooth root radius of the pinion toothing, and on the other hand over the tooth root radius of the ring gear toothing, ensure a constant counterforce. This will prevent it from varying pressures between the faces 56.1 . 56.2 ; 57.1 . 57.2 the teeth 28 . 31 and the axial disc 58.1 . 58.2 , which would result in an axial plate without these pressure kidneys, it comes in this area to changing compensation forces. An exact adaptation of the axial compensation is achieved by a computational and empirical determination and determination of the relief diameter of pinion 26 and ring gear 30 reached. The or each thrust washer 58.1 . 58.2 preferably has two openings 94.1 . 95.1 ; 94.2 . 95.2 on. Through these breakthroughs 94.1 . 95.1 ; 94.2 . 95.2 The pressure fluid flows from the input side to the pressure kidney 62.1 . 62.2 and vice versa from the print kidney 62.1 . 62.2 over the pressure fields 61.1 . 61.2 to the print output. In the embodiment, the respective bridge is located 93.1 . 93.2 approximately at the level of the center of the pinion and has a cross-section that is dimensioned such that about 50% of the hydraulic force caused by the operating pressure in the pressure kidney 62.1 . 62.2 and the breakthroughs 94.1 . 95.1 ; 94.2 . 95.2 , is recorded. Transition radii at the openings reduce the notch stress and thus increase the permissible operating pressures and increase the service life of the hydraulic machine 21 , The or each thrust washer 58.1 . 58.2 is usually made of brass or aluminum, but can also be made by a sintering process or by metal powder injection molding (MIM technique). To reduce the friction, a corresponding friction-minimized coating is advantageously applied.

The radial expansion of the pressures, as already described, by the control grooves 63.1.1 . 63.1.2 ; 63.2.1 . 63.2.2 ; 63.3.1 . 63.3.2 and control slots 64.1.1 . 64.1.2 ; 64.2,1 . 64.2.2 as well as through the V-shaped open space 85 and at the tooth mesh 33 achieved by the seal along the engagement line. The fixation of the respective axial plate 58.1 . 58.2 on the one hand by supernatant of the shaft 23 bearing bushes on the inner diameter and at the through hole retaining pins or bolts 45.1 . 45.2 on the outer circumference of the respective retaining pin or bolt 45.1 . 45.2 , In the axial direction 39 is the respective axial plate 58.1 . 58.2 freely movable within the intended axial play. The over the axial disc or plate 58.1 . 58.2 resulting leakage oil and the leakage oil above the sealing roller 49.1 . 49.2 accumulates in the area of the V-shaped open space 85 as well as in the annulus, passing through the chamfer 96 the respective axial sealing disc 58.1 . 58.2 on the ring gear 30 is formed and in the so-called leakage channel annulus 101.1 . 101.2 , with the bevel 97 the respective axial sealing disc 58.1 . 58.2 on the pinion 26 is formed. About a hole 98 as well as a groove 99 in the connection room 106 This leakage oil is partially conducted. A large or substantial part of the total leakage oil flows through radial bores 100.1 . 100.2 in the shaft (pump motor shaft) 23 , in the area of the respective annulus 101.1 . 101.2 arranged in a well as a leakage wave channel designated, centric, axially mounted relief bore 102 the wave 23 (please refer 2 . 11 and 12 ). It is understood that the bore 98 and / or the groove 99 could also be omitted. In this latter case, all the leakage oil would pass over the radial bores 100.1 . 100.2 the wave 23 in the leakage wave channel 102 flow. As a result, the flow velocity or the flow of the leaking oil in the canned space could 107 or in the leakage channel loop 108 be maximized. With "canned space" 107 is that space referred to, in the radial direction 109 considered inside or inside the sealing or gap tube 110 and the through the sealing or canned 110 is limited radially outward. By the above measures an even better heat dissipation could be achieved. At the same time could even better lubrication of the engine bearing 111 be achieved. This could have an even longer life or an even longer trouble-free operation of the motor-pump unit 20 be achieved. In the pump cover 25.1 is a bleed screw for filling and bleeding the complete hydraulic system 103 appropriate. The relief hole 102 is in the range of in the engine flange 25.4 arranged radial ball bearing 111 by a Lagerbefestigungs- or sensor screw made of a non-magnetic material, also referred to as a closure means 112 closed and opens into a radially mounted hole 113 , This radial bore 113 opens into an annular space, also referred to as a connection space 114 ,

Overall structure of the motor-pump unit:

• 1. Magnetkupplung zwischen Pumpe und Motor
• 2. Spalttopfmotor – Motor unter Öl
• 3. Kompletter Motor unter Öl mit druckfesten Stromdurchführungen

The requirement for absolute tightness can only be achieved by a hermetically sealed system. There are three ways to do this:

• 1. Magnetic coupling between pump and motor
• 2. Split pot motor - engine under oil
• 3. Complete motor under oil with pressure-resistant current feedthroughs

The magnetic coupling is eliminated for space and cost reasons. For the preferred application of the motor-pump unit 20 became a special engine 22 with a "split tube", also referred to as a sealing tube 110 developed. The term "canned" stems from the fact that this tube 110 between the rotor 22.1 and the stator 22.2 is arranged. The sealing or gap tube 110 consists of a non-magnetic material, preferably of a high-temperature resistant, pressure-resistant, fiber-reinforced plastic. The sealing tube 110 extends almost the entire length of the stator and is with the stator 22.2 including winding and motor housing 25.3 shed with plastic into one unit. On the side facing the pinion of the sealing or gap tube 110 protrudes the lid or housing part 25.2 with a corresponding centering collar 115 with O-ring groove 116 into the sealing or gap tube 110 , On the facing away from the pinion side of the sealing or gap tube 110 protrudes one with the motor flange or housing part 25.4 bolted bearing fixing screw 117 with a corresponding centering collar 118 with O-ring groove 119 into the sealing or gap tube 110 , In the O-ring grooves 116 . 119 recorded O-rings, which are not shown in the figures, take over the sealing function, so seal the canned space 107 on both sides of the rotor 22.1 at least leak-tight from.

The common motor-pump shaft 23 carries the pressed rotor 22.1 , includes pressure compensation holes and the bearing mounting or sensor screw 107 for receiving a speed sensor 120 , The motor-pump shaft 23 is motor side only on or in the radial ball bearing 111 and on the pump side or in at least one sliding bearing, preferably on or in two plain bearings 121.1 . 121.2 stored. The pinion 26 the pump or hydraulic machine 21 is provided by a clearance fit on the pump motor shaft 23 stored and by the slightly longitudinal ball key 37 taken with it. The inner ring 122.1 of the ball bearing 111 is through the bearing mounting and sensor screw 112 firmly with the motor pump shaft 23 connected. The outer ring 122.2 of the ball bearing 111 is with the bearing mounting screw 117 with the electronics side bearing cover or housing part 25.4 screwed. This is the motor pump shaft 23 fixed axially and thus also the pressed rotor 22.1 , The bearing cap 25.4 has a specially stepped blind hole 123 on, in which the bearing mounting and sensor screw 112 protrudes. The signal transmission takes place through the closed bearing cover or housing part 25.4 in the area of the sensor 120 has a wall thickness of a few millimeters. Preferably, the wall thickness is about 2 mm. On the from the engine 22 opposite side of the bearing cap or housing part 25.4 is in a housing part in the form of a flange 25.5 the electronic board 124 of the speed sensor 120 arranged and at a certain axial distance to a two-sided populated board 125 the motor controller, here the power amplifier 126 , On this power amplifier 126 a regulator board is arranged. The phase lines 127 (please refer 1 ) of the motor 22 lead preferably through holes in the housing part or bearing cap 25.4 and are at the power amp 126 screwed, plugged or soldered. Similarly arranged are sensor lines of temperature sensors, which are the winding temperatures of the motor 22 measure up. The connection of the motor-pump unit 20 via a power connector 128 and a small sized signal connector 129 , The two plugs 128 . 129 are sealed to the electronics box 130 appropriate. The electronics box 130 is with a tubular housing part 25.6 and with a lid designed as a housing part 25.7 and with the tubular, also referred to as a bearing cap or motor flange housing part 25.4 educated. The electronics box 130 with cooling fins 131 is also screwed on. Between the individual elements of the electronics box 130 are also arranged sealing elements. The final stage 126 is on a, preferably made of copper, receiving angle 132 mounted with thermal grease. As a result, the heat development of the components by the copper angle 132 in the cooling fins 131 of the tubular housing part 25.6 the electronics box 130 directed. Also with cooling fins 131 provided are the lid 25.6 the electronics box 130 and the tubular motor housing 25.3 , The intermediate housing of the hydraulic machine also provides the bearing cap 25.4 or motor flange of the electric motor 22 The hydraulic machine is a compensated 4-quadrant internal gear machine 21 executed and is essentially with the interior of the sealing or gap tube 110 fluidly connected.

In particular for the application or for the use of the motor-pump unit 20 For driving or operating a highly dynamic hydraulic axis has an electric motor 22 in the form of a brushless DC motor (EC motor) proved to be particularly advantageous. Like from the 12 and 14 as can be seen, the rotor comprises 22.1 of the electric motor 22 a plurality of recesses also referred to as leakage rotor channels 133.1 . 133.2 . 133.3 . 133.4 . 133.5 , Preferably, these are in the same circumferential angles about the rotor axis of rotation 33.1 or about the shaft rotation axis 35 arranged offset from one another. In the embodiment shown, there are five leakage rotor channels 133.1 . 133.2 . 133.3 . 133.4 . 133.5 , intended. Furthermore, the rotor comprises 22.1 a plurality of high performance magnets 134 , preferably permanent magnets. The magnets 134 are in the same circumferential angles around the rotor axis of rotation 34.1 or about the shaft rotation axis 35 staggered. In the geigte embodiment are ten magnets 134 intended. As in particular from 15 As can be seen, the magnets are 134 on its radially outward from the rotor axis of rotation 34.1 or from the shaft rotation axis 35 away facing outer surface with a tubular bandage 135 Mistake. This bandage 135 limits the rotor 22.1 radially outward on its outer circumference. The rotor 22.1 is in a cylindrical receiving space 136 of the stator 22.2 rotatably mounted relative to this. Also in the cylindrical storage room 136 of the stator 22.2 but in the radial direction 109 considered between the rotor 22.1 and the stator 22.2 This is also known as a sealing tube can 110 arranged firmly with the stator 22.2 connected is. In the radial direction 109 considered between the sealing or gap tube 110 and the rotor 22.1 is a narrow annular gap 137 formed, which also with leakage splitting channel 137 is designated. This ring channel 137 extends in the axial direction 39 , Preferably substantially over the entire axial length or over the entire axial length of the rotor 22.1 ,

The stator 22.2 includes an inner tube 138 and an outer tube 139 as well as several in the radial direction 109 between the inner tube 138 and the outer tube 139 and also in the axial direction 39 extending webs 140 at one end with the inner tube 138 and at the other end with the outer tube 139 are connected. In the embodiment shown are preferably twelve webs 140 provided (see 14 ). How out 12 can be seen, the webs 140 at its radially outer ends a recess 141 on, in the outer tube 139 of the stator 22.2 is arranged. In the axial direction 39 considered has the respective recess 141 an axial width or has the outer tube 139 an axial length that is slightly smaller than the axial length of the rotor 22.1 , The stator 22.2 is made of several stator laminations. Between neighboring bridges 140 of the bridges 140 , the inner tube 138 and the outer tube 139 of the stator 22.2 is each a recording room 142 educated. In the embodiment shown, therefore, according to the number of webs 140 preferably twelve receiving spaces 142 intended. Each recording room 140 serves to accommodate stator windings of metal wires, which are the phase lines 127 form. Furthermore, each recording room serves 142 for receiving potting material. The stator 22.2 is in a cylindrical stator-receiving space of the motor housing 25.3 of the housing 25 the motor-pump unit 20 and is fixed to the motor housing 25.3 connected.

In the housing part 25.2 the working chamber 24 the pump 21 limiting housing parts 25.1 . 25.2 of the housing 25 is at least one with the working chamber 24 Fluidverbunder, preferably designed as an annulus, leakage channel 101.1 . 101.2 arranged over which in the operation of the internal gear pump 21 under pressure along the axial and radial sealing surfaces resulting leakage oil is derived. In other words, the at least one leakage channel is used 101.1 . 101.2 for the derivation of a during operation of the internal gear machine 21 , Especially with a radial and / or Axialspaltabdichtung means of Radialdichtsegmente 43.1 . 43.2 and / or the at least one axial sealing plate 58.1 . 58.2 , forming, consisting of the fluid pressure medium, leakage fluids. The leakage channel in particular acts in each axial sealing plate 58.1 . 58.2 trained annular space 101.1 . 101.2 in the axial direction 39 to the working chamber 24 is open and in the radial direction 109 to the wave 23 is open (see 2 . 4 and 11 ).

The wave 23 extends with a shaft end 23.1 their two shaft ends 23.1 . 23.2 from the pinion 26 away in the axial direction 39 by the one from the wave 23 worn rotor 22.1 , The in the housing part 25.1 of the housing 25 arranged connection channels 105.1 . 105.2 are over in the case 25 or in one the working chamber 24 the internal gear machine 21 limiting housing part 25.2 of the housing 25 arranged check valves 143.1 . 143.2 with the with the at least one leakage channel 101.1 . 101.2 fluid-connected leakage channel loop 108 connected. The leakage channel loop 108 extends over that of the pinion 26 away extending rotor end 144.1 of the rotor 22.1 out. The leakage channel loop 108 points in the axial direction 39 in the wave 23 or by the wave 23 extending, also referred to as a relief bore leakage wave channel 102 and at least one with the leakage wave channel 102 fluidly connected, at a radial distance to the leakage wave channel 102 , in the axial direction 39 through the rotor 22.1 extending through the leakage rotor channel 133.1 . 133.2 . 133.3 . 133.4 . 133.5 of the rotor 22.1 and also with the leakage wave channel 102 fluidly connected, in the radial direction 109 considered between the rotor 22.1 and the stator 22.2 trained, in the axial direction 39 extending leakage gap channel 137 on. The check valves 143.1 . 143.2 open in a fluid flow direction from the leakage channel loop 108 to the respective active low pressure region of the working chamber 24 and block in an opposite direction or in an opposite direction of fluid flow from the respective active high-pressure region of the working chamber 24 to the leakage channel loop 108 , As a result, during operation of the internal gear pump 21 achieved that the leakage fluid from the at least one leakage channel 101.1 . 101.2 through the leakage channel loop 108 in the working chamber 24 flows. From there, the leakage fluid essentially flows into the connection channel assigned to the respectively active low-pressure region, that is, except for a small leakage current component which is small in comparison to the total leakage flow 105.1 . 105.2 ,

In other words, it can be provided according to the invention that in the shaft 23 in the axial direction 39 extending leakage wave channel 102 is arranged, with the at least leakage channel 101.1 . 101.2 fluid-connected, and that in the rotor 22.1 at least one, preferably at a radial distance, in particular parallel, to the leakage wave channel 102 , in the axial direction 39 through the rotor 22.1 extending leakage rotor channel 133.1 . 133.2 . 133.3 . 133.4 . 133.5 is arranged with the leakage shaft channel 102 fluidly connected and / or that one, in the radial direction 109 considered between the rotor 22.1 and the stator 22.2 trained, in the axial direction 39 extending leakage gap channel 137 with the leakage wave channel 102 fluidly connected, and that the leakage wave channel 102 or the leakage rotor channel 133.1 . 133.2 . 133.3 . 133.4 . 133.5 and / or the leakage gap channel 137 about one in the case 25 or in one the working chamber 25 limiting housing part 25.2 of the housing 25 arranged first check valve 143.1 with the first connection channel 105.1 and about one in the case 25 or in one or the working chamber 24 limiting housing part 25.2 arranged second check valve 143.2 with the second connection channel 105.2 is connected, and that upon rotation in the first operating direction 104.1 the first check valve 143.1 a fluid flow of the fluid pressure medium from the then active first high-pressure region 44.1 the working chamber 24 over the first check valve 143.1 in the leakage wave channel 102 or in the leakage rotor channel 133.1 . 133.2 . 133.3 . 133.4 . 133.5 and / or in the leakage gap channel 137 prevents and the second check valve 143.2 a fluid flow of the leakage fluid from either the leakage shaft passage 102 or from the leakage rotor channel 133.1 . 133.2 . 133.3 . 133.4 . 133.5 and / or from the leakage gap channel 137 over the second check valve 143.2 in the then active first low pressure area 44.1 the working chamber 24 permits, and that upon rotation in the second operating direction 104.2 the second check valve 143.2 a fluid flow of the fluid pressure medium from the then active second high-pressure region 44.2 the working chamber 24 over the second check valve 143.2 in the leakage wave channel 102 or in the leakage rotor channel 133.1 . 133.2 . 133.3 . 133.4 . 133.5 and / or in the leakage gap channel 137 stops and the first check valve 143.1 a fluid flow of the leakage fluid from either the leakage shaft passage 102 or from the leakage rotor channel 133.1 . 133.2 . 133.3 . 133.4 . 133.5 and / or from the leakage gap channel 137 over the first check valve 143.1 in the then active second low pressure range 44.2 the working chamber 24 allows, so that when rotating in the first operating direction 104.1 the leakage fluid, preferably in a leakage fluid circuit, of the at least one leakage channel 101.1 . 101.2 either through the leakage wave channel 102 and from there through the leakage rotor channel 133.1 . 133.2 . 133.3 . 133.4 . 133.5 and / or through the leakage gap channel 137 , or vice versa, via the second check valve 143.2 in the then active first low pressure area 44.1 the working chamber 24 flows and during rotation in the second operating direction 104.2 the leakage fluid, preferably in a leakage fluid circuit, of the at least one leakage channel 101.1 . 101.2 either through the leakage wave channel 102 and from there through the leakage rotor channel 133.1 . 133.2 . 133.3 . 133.4 . 133.5 and / or through the leakage gap channel 137 , or vice versa, via the first check valve 143.1 in the then active second low pressure range 44.2 the working chamber 24 flows.

Shuttle valves / check valves:

The 12 shows a longitudinal section through the gear machine 21 in the area of two arranged check valves 143.1 . 143.2 , The check valves 143.1 . 143.2 , which are also referred to with shuttle valves, have the task of the canned space 107 always with the working connections or connection channels 105.1 and 105.2 to connect such that the lowest possible pressure in the canned space 107 prevails. The described motor-pump unit 20 is preferably used in a closed hydraulic system not shown in the figures. This hydraulic system, in addition to a, for example, double or single-acting hydraulic cylinder and a, preferably designed as a diaphragm pressure accumulator contain pressure accumulator, which can compensate for volume changes by different piston surfaces and by temperature fluctuations or compensates. The accumulator ensures a certain system or preload pressure. Preferably, the system or biasing pressure is in the range of 5 to 40 bar. The working pressure of the internal gear machine 21 is superimposed on this preload or system pressure. The working pressure can be up to 120 bar or even up to 250 bar or more. The shuttle valves 143.1 . 143.2 now have the task to ensure that always only the lower pressure in the canned space 107 prevails. The shuttle valves 143.1 . 143.2 are each located in one in the respective pressure field 61.1 . 61.2 , for example here of the housing part 25.2 (please refer 7 and 13 ), preferably formed as a blind bore, as a channel part of a return flow channel 154.1 . 154.2 designated axial bore 145.1 . 145.2 (please refer 12 and 13 ). In each case a diagonal bore 146.1 . 146.2 of the respective return flow channel 154.1 . 154.2 connects the bore base of the respective axial bore 145.1 . 145.2 with the canned space 107 over the connection room 106 (please refer 12 and 13 ). At the shuttle valves 143.1 . 143.2 These are commercially available spring-loaded check valves with a ball 147 as a sealing or blocking element and with a spring 148 , by means of which the ball 147 is biased in its sealing or blocking position. The ball 147 and the spring 148 are in a guiding element 149 stored. The guide element 149 is in the respective axial bore 145.1 . 145.2 pressed in and secured with a locking sleeve. Depending on the direction of rotation 104.1 . 104.2 now arises in one of the pressure fields 61.1 . 61.2 a higher pressure. This closes this pressure field 61.1 . 61.2 associated sealing or blocking element (ball) 147 one of the shuttle valves 143.1 . 143.2 , In an operating direction in the first direction of rotation 104.1 So closes that then the pressurized fluid with high pressure field 61.1 assigned shuttle valve 143.1 and at an operating direction in the second rotational direction 104.2 then closes the then applied with fluid high pressure pressure field 61.2 assigned shuttle valve 143.2 ,

Under pressure arises in the, preferably axially and radially compensated, internal gear pump 21 Leakage oil along the axial and radial sealing surfaces. This leakage oil collects in open spaces 85 and annular spaces 96 . 101.1 . 101.2 , especially in the axial discs 58.1 . 58.2 (please refer 4 ). By the one with the at least one annulus 101.1 . 101.2 fluid-connected radial bores 38.1 . 38.2 in the motor pump shaft 23 (please refer 2 and 11 ), the leakage oil flows into the axial relief hole, also referred to as a leakage shaft channel 102 in the pump shaft 23 and from this again via the radial bore 113 and via the so-called leakage rotor channels recesses 133.1 . 133.2 . 133.3 . 133.4 . 133.5 in the rotor 22.1 or via the also as a leakage gap channel 137 designated annular gap between the rotor 22.1 and the stator 22.1 , specifically between the bandage 135 of the rotor 22.1 and also referred to as a sealing tube, fixed to the stator 22.2 connected can 110 , back to the connection room 106 , In view of the preferably very small gap width of this annular gap or leakage gap channel 137 and the plurality and each having a comparatively large passage cross-section, also referred to as leakage rotor channels recesses 133.1 . 133.2 . 133.3 . 133.4 . 133.5 of the rotor 22.1 However, most of the total leakage oil flows through the leakage rotor channels 133.1 . 133.2 . 133.3 . 133.4 . 133.5 back to the connection room 106 , This arises in the connection room 106 a slight overpressure, which eventually depends on the direction of rotation 104.1 . 104.2 the shuttle valve 143.1 . 143.2 in the lower pressure loaded pressure field 61.1 . 61.2 opens. Through the open shuttle valve 143.1 . 143.2 Thus, a connection between the input side, so the system or bias pressure, and the canned space 107 produced. The preload pressure or system pressure can be many times lower than the working pressure. By this advantageous arrangement of the shuttle valves according to the invention 143.1 . 143.2 can the stator 22.2 the motor-pump unit 20 and also the two cover or housing parts 25.2 . 25.4 be carried out advantageously cheaper, since these components do not have to withstand the high working pressure.

By the above-described leakage oil guide is also ensured that the motor side arranged ball bearings 111 is supplied with oil. This will make this camp 111 smeared that Frictional heat removed and thus significantly increases the life. In the example shown, the radial bore opens 113 on the ball bearing side though, from the pinion 26 From the perspective of the ball bearing 111 but is with the between the inner ring 122.1 and the outer ring 122.2 of the ball bearing 111 formed bearing gap 155 fluidly connected (see 11 and 12 ), so that nevertheless reaches both a sufficient lubrication and a cooling effect and removes frictional heat. An improvement in the bearing lubrication could be achieved by an axial bore not shown in the figures and an additional, also not shown in the figures, radial bore in the Lagerbefestigungs- or sensor screw. These additional holes may be in addition to that of the pinion 26 Seen from the warehouse 111 or before the Lagerbefestigungs- or sensor screw 112 arranged radial bore 113 in the motor pump shaft 23 or alternatively, so instead, be attached. As a result, an advantageous forced lubrication of the bearing 111 be achieved.

Common wave:

In the preferred embodiment shown in the figures, there is a one-piece or one-piece motor-pump shaft 23 shown. According to an alternative solution, which is not shown in the figures, separate shafts in the form of a pump shaft and a motor shaft could also be provided. An entrainment could be done by a spline, for example, with a head or Fußzentrierung to fix the two waves. A fixation of the two waves could also be done via an additional fit between the motor and pump shaft. In order to maintain the leakage oil circuit, as described above, then both the motor shaft and the pump shaft would have to have an axial leakage shaft channel or an axial relief bore, which would have to be fluidly connected to one another.

Bearing fixing and sensor screw:

Preferably, the Lagerbefestigungs- and sensor screw 112 made of a non-magnetic material to the magnetic signals of the sensor 120 not to influence. The sensor 120 is in an axial bore 150 the bearing mounting and sensor screw 112 attached, preferably glued. The outer diameter of the bearing mounting and sensor screw 112 is larger than the inner diameter of the ball bearing 111 or its inner ring 122.1 , This is an axial fixation of the ball bearing 111 or the motor pump shaft 23 at the ball bearing 111 , The sensor screw 112 is offset at its outer diameter and encloses the sensor 120 with a thin-walled tubular part 151 , This tubular part 151 with sensor 120 protrudes into a blind hole 152 in the housing or cover part 25.4 , The bottom of the blind hole 152 has a residual wall thickness of a few millimeters, preferably about 2 mm. By this advantageous embodiment of the housing or cover part 25.4 can the engine-pump unit 20 be loaded with a high system pressure, preferably up to 200 bar. The low residual wall thickness of the floor or wall part 153 of the sensor 120 containing tubular part 151 the bearing mounting and sensor screw 112 influences the magnetic flux of the sensor 120 to a limited extent. Preferably, the bore 150 in the housing or cover part 25.4 only slightly larger than the outer diameter of the tubular part 151 the bearing mounting and sensor screw 112 , As a result, the pressurized surface of the low residual wall thickness having soil or wall portion 153 of the tubular part 151 ideally kept as small as possible.

LIST OF REFERENCE NUMBERS

20

 Motor-pump unit

21

 Internal Gear Machine / Internal Gear Pump / Hydraulic Pump / Gear Machine / Hydraulic Machine

22

 electric motor

22.1

Rotor of 22

22.2

Stator of 22

23

 Shaft / motor pump shaft

23.1

 shaft end

23.2

 shaft end

24

 working chamber

25

 casing

25.1

 Lid or housing part

25.2

 Housing part / lid part

25.3

 Housing part / motor housing

25.4

 Housing part / lid part / motor flange / bearing cap

25.5

 Housing part / lid part / flanging

25.6

 housing part

25.7

 Housing part / cover / lid

26

 Gear / pinion

27

 bearing ring

28

 Dental / pinion

29

 Gap / pinion tooth gap

30

 ring gear

31

 Dental / Hohlradzahn

32

 Gear gap / Hohlradzahnlücke

33

 Meshing area / tooth engagement

34.1

 Rotary axis / rotor axis of rotation

34.2

 Axis of rotation / pinion axis of rotation

35

 Shaft axis of rotation

36

 Axis of rotation / Hohlraddrehachse

37

 Adjusting spring

38.1

 groove

38.2

 groove

39

 axially

40

 free space

41

 filling

42

 Segment / radial sealing segment / sprocket segment / segment support

43.1

 Sealing segment / radial sealing segment / ring gear segment

43.2

 Sealing segment / radial sealing segment / ring gear segment

44.1

 (first) area / (active) high-pressure area or low-pressure area / high-pressure space / low-pressure space

44.2

 (second) area / (active) high pressure area or low pressure area / high pressure room / low pressure room

45.1

 Retaining pin / retaining bolt

45.2

 Retaining pin / retaining bolt

46

Outer surface of 42

47.1

Outer surface of 43.1

47.2

Outer surface of 43.2

48.1

 Recess / Dichtrollennut

48.2

 Recess / Dichtrollennut

49.1

 seal roller

49.2

 seal roller

50.1

 Sealing roller spring

50.2

 Sealing roller spring

51.1

 Segmentfedernut

51.2

 Segmentfedernut

52.1

 Spring / spring element

52.2

 Spring / spring element

53.1

 Pinion segment end

53.2

 Pinion segment end

54.1

 Stop / stop pocket

54.2

 Stop / stop pocket

55.1

 stop surface

55.2

 stop surface

56.1

Face of 26

56.2

Face of 26

57.1

Face of 30

57.2

Face of 30

58.1

 Axialdichtplatte / Axialdichtscheibe / thrust washer

58.2

 Axialdichtplatte / Axialdichtscheibe / thrust washer

59.1

Inside surface of 58.1

59.2

Outer surface of 58.1

60.1

Inside surface of 58.2

60.2

Outer surface of 58.2

61.1

Control field / recess / axial field / pressure field / axial pressure field in 25.1

61.2

Control field / recess / axial field / pressure field / axial pressure field in 25.1

62.1

Control panel / sealing plate recess / pressure kidney in 58.1

62.2

Control panel / sealing plate recess / pressure kidney in 58.1

63.1.1

 (first) tax credit

63.1.2

 (first) tax credit

63.2.1

 (second) tax rate

63.2.2

 (second) tax rate

63.3.1

 (third) (seal plate) cam groove / seal plate) control channel / recess / recess / control channel

63.3.2

 (third) (seal plate) cam groove / (seal plate) control channel / recess / recess / control channel

64.1.1

 control slot

64.1.2

 control slot

64.2.1

 control slot

64.2.2

 control slot

65

 Radial sealing segment control channel

65.1

 chamfer

65.2

 chamfer

65.3

 (Tax) groove

65.4

 (Tax) groove

65.5

 chamfer

65.6

 chamfer

66

 angle

67.1

 open space

67.2

 open space

68.1

(Receiving) hole from 25.1

68.2

(Receiving) hole from 25.2

69.1

 guide region

69.2

 guide region

70

 angle

70.1

 angle

71.1

 Contact surface / retaining body-supporting surface

71.2

 Contact surface / retaining body-supporting surface

71.3

 Contact surface / sealing segment support surface

71.4

 Contact surface / sealing segment support surface

72

Inner surface / outer peripheral surface of 42

73.1

Inner surface / inner peripheral surface / sealing surface of 43.1

73.2

Inner surface / inner peripheral surface / sealing surface of 43.2

74

 electronics

75.1

 Gap / radial clearance / gap

75.2

 Gap / radial clearance / gap

76.1

 paragraph

76.2

 paragraph

77.1

Face of 76.1

77.2

Face of 76.2

78.1

Face of 45.1

78.2

Face of 45.2

79.1

Groove bottom of 80.1

79.2

Groove bottom of 80.2

80.1

 (Pinion -) (segment) groove

80.2

 (Pinion -) (segment) groove

81

 radius

82

 chamfer

83

 radius

84.1

Side surface of 85

84.2

Side surface of 85

85

 V-shaped open space

86.1

Holding body / part of 45.1

86.2

Holding body / part of 45.2

87

 plane of symmetry

88

 Focus

89

 Focus

90

 (Axial -) (ring) seal

91

 support ring

92

(Cross) bridge of 91

93.1

 (Transverse) web

93.2

 (Transverse) web

94.1

 breakthrough

94.2

 breakthrough

95.1

 breakthrough

95.2

 breakthrough

96

 Chamfer / annulus

97

 Chamfer / annulus

98

 drilling

99

 groove

100.1

 Radial recess / (radial) bore

100.2

 Radial recess (radial) bore

101.1

 Annulus / leakage channel

101.2

 Annulus / leakage channel

102

 Leak-wave channel / relief well

103

 bleed screw

104.1

 first operating or direction of rotation

104.2

 second operating or direction of rotation

105.1

 (first) connection channel

105.2

 (second) connection channel)

106

 communication space

107

 Canned room

108

 Leakage channel loop

109

 radial direction / radial direction

110

 Sealing or gap tube

111

 (Motor / rotor) Storage / (radial) Ball bearing

112

 Bearing mounting or sensor body / bearing mounting or sensor screw

113

 Bore / radial recess / radial bore

114

 Communication space / annulus

115

Centering collar of 25.2

116

 O-ring groove

117

 Bearing mounting bolt

118

Centering collar of 117

119

 O-ring groove

120

 (Speed) sensor

121.1

 bearings

121.2

 bearings

122.1

Inner ring of 111

122.2

Outer ring of 111

123

 (stepped) bag hole

124

 electronic board

125

 circuit board

126

 final stage

127

 phase lines

128

 power connector

129

 signal connector

130

 electronics box

131

 cooling fin

132

 Shooting angle / copper angle

133.1

 Leakage rotor channel / recess

133.2

 Leakage rotor channel / recess

133.3

 Leakage rotor channel / recess

133.4

 Leakage rotor channel / recess

133.5

 Leakage rotor channel / recess

134

 (High performance) magnet / permanent magnet

135

 bandage

136

 accommodation space

137

 Leakage gap channel / leakage ring gap channel Annular gap / ring channel

138

 inner tube

139

 outer tube

140

 web

141

 recess

142

 accommodation space

143.1

 Check valve / shuttle valve

143.2

 Check valve / shuttle valve

144.1

 rotor end

144.2

 rotor end

145.1

 (first) bag axial bore / (first) channel part

145.2

 (second) bag / axial bore / (second) channel part

146.1

 oblique bore

146.2

 oblique bore

147

 Bullet

148

 feather

149

 guide element

150

 (axial) bore

151

(tubular) part of 112

152

 blind hole

153

Ground of 152 / Wall part of 151

154.1

 (first) return flow channel

154.2

 (second) return flow channel

155

Bearing gap of 111

Claims (21)

Motor-pump unit with a multi-part housing ( 25 ), which is an internal gear machine ( 21 ) for reversing operation and an electric motor ( 22 ), which has at least one in the housing ( 25 ) about a shaft rotation axis ( 35 ) rotatably mounted shaft ( 23 ) with the internal gear machine ( 21 ), wherein the electric motor ( 22 ) one in a housing part ( 25.3 ) of the housing ( 25 ) arranged around a rotor axis ( 34.1 ) rotatable rotor ( 22.1 ) and a stator ( 22.2 ), and wherein the internal gear machine ( 21 ) a working chamber ( 24 ) comprising at least two housing parts ( 25.1 . 25.2 ) of the housing ( 25 ) is limited and in the two gears ( 26 . 30 ), which are a pinion teeth ( 28 ) having external toothed pinion ( 26 ) and a ring gear teeth ( 31 ) having internally toothed ring gear ( 30 ), which with respect to the pinion ( 26 ) is mounted eccentrically, wherein ring gear teeth of the ring gear teeth ( 31 ) of the ring gear ( 30 ) in a meshing area ( 33 ) with pinion teeth of the pinion teeth ( 28 ) of the pinion ( 26 ), and wherein the pinion ( 26 ) by one Pinion rotation axis ( 34 .2) and the ring gear ( 30 ) about a parallel to the pinion axis ( 34.2 ) arranged Hohlraddrehachse ( 36 ) are rotatably mounted, and wherein the Hohlraddrehachse ( 36 ) and the pinion axis ( 34.2 ) in an axial direction ( 39 ), and wherein between the pinion ( 26 ) and the ring gear ( 39 ) a crescent-shaped space ( 40 ) is formed, in which a multipart filler ( 41 ) is arranged, the plurality of radially movable relative to each other radial sealing segments ( 42 ; 43.1 . 43.2 ) for the radial sealing of a high pressure area ( 44.1 . 44.2 ) of the working chamber ( 24 ), of which a first radial sealing segment on one of pinion teeth of the pinion teeth ( 28 ) of the pinion ( 26 ) engageable or adjacent pinion segment ( 42 ) and of which a second Radialdichtsegment a at Hohlradzähnen the Hohlradzähne ( 31 ) of the ring gear ( 30 ) can be applied or applied ring gear segment ( 42.1 . 42.2 ), and wherein between a radially outward to the ring gear segment ( 42.1 . 42.2 ) facing inner surface ( 72 ) of the pinion segment ( 42 ) and one of these opposite, radially inwardly to the pinion segment ( 42 ) facing inner surface ( 73.1 . 73.2 ) of the ring gear segment ( 42.1 . 42.2 ) a radial gap ( 75.1 . 75.2 ), and wherein between axial Stirnfächen ( 56.1 . 57.1 ; 56.2 . 57.2 ) of the gears ( 26 . 30 ) and at least one housing part ( 25.1 . 25.2 ) of the housing ( 25 ) at least one in the axial direction ( 39 ) movable axial sealing plate ( 58.1 . 58.2 ) for the axial sealing of the high pressure area ( 44.1 . 44.2 ) of the working chamber ( 24 ), characterized in that the at least one Axialdichtplatte ( 58.1 . 58.2 ) on their faces ( 56.1 . 57.1 ; 56.2 . 57.2 ) of the gears ( 26 . 30 ) pointing side at least one of the end faces ( 56.1 . 57.1 ; 56.2 . 57.2 ) of the gears ( 26 . 30 ) open towards the sealing plate recess in the form of a pressure medium acted upon sealing plate control channel ( 63.3.1 . 63.3.2 ) leading to the radial gap ( 75.1 . 75.2 ) is open and the radial gap ( 75.1 . 75.2 ) is directly opposite and / or that the pinion segment ( 42 ) and / or the ring gear segment ( 43.1 . 43.2 ) at least one radial-sealing-segment depression in the form of a groove in a circumferential direction about the axis of rotation of the pinion (US Pat. 34.2 ) or about the Hohlraddrehachse ( 36 ) extending, can be acted upon with pressure medium or with the pressure medium Radialdichtsegment control channel ( 65 ) facing the radial gap ( 75.1 . 75.2 ) is open and directly into the radial gap ( 75.1 . 75.2 ) opens. Motor-pump unit according to claim 1, characterized in that the pinion segment ( 42 ) and / or the ring gear segment ( 43.1 . 43.2 ) one in the axial direction ( 39 ) extending sealing roller groove ( 48.1 . 48.2 ) in which one in the radial direction relative to the pinion segment ( 42 ) and to the ring gear segment ( 43.1 . 43.2 ) movable sealing roll ( 49.1 . 49.2 ) for sealing the radial gap ( 75.1 . 75.2 ) between the pinion segment ( 42 ) and the ring gear segment ( 43.1 . 43.2 ) and that the pinion segment ( 42 ) and / or the ring gear segment ( 43.1 . 43.2 ) one in the axial direction ( 39 ) extending segment spring groove ( 51.1 . 51.2 ), which at a circumferential distance to the sealing roller groove ( 48.1 . 48.2 ) in the direction of a high pressure area ( 44.1 . 44.2 ) associated pinion segment end ( 53.1 . 53.2 ) of the pinion segment ( 42 ) or Hohlradsegmentendes the Hohlradsegments offset, wherein in the segment spring groove ( 51.1 . 51.2 ) a prestressed spring ( 52.1 . 52.2 ) is arranged, by means of which the Hohlradsegment ( 43.1 . 43.2 ) and the pinion segment ( 42 ) are pressed away from each other in the radial direction such that the pinion segment ( 42 ) with a radially inwardly facing outer surface ( 46 ) on pinion teeth of the pinion teeth ( 31 ) of the pinion ( 26 ) and that the ring gear segment ( 43.1 . 43.2 ) with a radially outwardly facing outer surface ( 47.1 . 47.2 ), from the outer surface ( 46 ) of the pinion segment ( 42 ) away, at Hohlradzähnen the Hohlradzähe ( 31 ) of the ring gear ( 30 ) and / or that the pinion segment ( 42 ) as a segment carrier for the ring gear segment ( 43.1 . 43.2 ) is formed and a stop ( 54.1 . 54.2 ) with one in the axial direction ( 39 ) and radially outward to the ring gear ( 30 ) extending stop surface ( 55.1 . 55.2 ) for supporting the ring gear segment ( 43.1 . 43.2 ) against retraction during operation of the internal gear machine ( 21 ) in the meshing area ( 33 ), the stop ( 54.1 . 54.2 ) with its stop surface ( 55.1 . 55.2 ) at a circumferential distance to the segment spring groove ( 51.1 . 51.2 ) in the direction of the high pressure area ( 44.1 . 44.2 ) associated pinion segment end ( 53.1 . 53.2 ) of the pinion segment ( 42 ) Is arranged offset or that the ring gear segment is formed as a segment carrier for the pinion segment and a stop having a in the axial direction and radially inwardly toward the pinion extending axial stop surface for supporting the pinion segment against retraction during operation of the internal gear machine in the tooth engagement region wherein the stop is arranged offset with its stop surface in a circumferential distance to the segment spring groove in the direction of the ring gear segment end of the ring gear segment assigned to the high-pressure region. Motor-pump unit according to claim 1 or 2, characterized in that the sealing plate control channel ( 63.3.1 . 63.3.2 ) is formed as a sealing plate control groove. Motor-pump unit according to one of the preceding claims, characterized in that the sealing plate control channel ( 63.3.1 . 63.3.2 ) in a direction parallel to the axial direction ( 39 ) extending cross-section considered a V-shaped cross-section. Motor-pump unit according to one of the preceding claims, characterized in that the sealing plate control channel ( 63.3.1 . 63.3.2 ) along the radial slot ( 75.1 . 75.2 ). Motor-pump unit according to one of the preceding claims, characterized in that the sealing plate control channel ( 63.3.1 . 63.3.2 ) extends in the circumferential direction. Motor-pump unit according to one of the preceding claims, characterized in that the sealing plate control channel ( 63.3.1 . 63.3.2 ) has a control channel length, via which it leads to the radial slot ( 75.1 . 75.2 ) and the radial slot ( 75.1 . 75.2 ) is directly opposite over its entire control channel length. Motor-pump unit according to one of the preceding claims, characterized in that the sealing plate control channel ( 63.3.1 . 63.3.2 ) into a substantially in the high pressure area ( 44.1 . 44.2 ) arranged, acted upon by pressure medium sealing plate recess ( 62.1 . 62.2 ) of the axial sealing plate ( 58.1 . 58.2 ), which leads to the axial end faces ( 56.1 . 57.1 ; 56.2 . 57.2 ) of the gears ( 26 . 30 ) and is directly opposite. Motor-pump unit according to claim 8, characterized in that the sealing plate control channel ( 63.3.1 . 63.3.2 ) starting from the sealing plate recess ( 62.1 . 62.2 ) along the radial slot ( 75.1 . 75.2 ). Motor-pump unit according to claim 8 or 9, characterized in that the sealing plate control channel ( 63.3.1 . 63.3.2 ) starting from the sealing plate recess ( 62.1 . 62.2 ) either along the radial slot ( 75.1 . 75.2 ) extends into a region which the segment spring groove ( 51.1 . 51.2 ) directly opposite or along the radial slot and the segment spring groove, the segment spring groove immediately opposite, extends into a region which is disposed either between the segment spring groove and the sealing roller groove or which extends to the sealing roller groove or which is directly opposite the sealing roller groove. Motor-pump unit according to one of the preceding claims, characterized in that the radial-sealing-segment control channel ( 65 ) extends in a direction in which the pinion ( 26 ) about its pinion axis ( 34.2 ) or in which the ring gear ( 30 ) about its Hohlraddrehachse ( 36 ) is rotatable and / or that the radial sealing segment control channel ( 65 ) in a direction perpendicular to the axial direction ( 39 ) extending in the direction of the imaginary plane. Motor-pump unit according to one of the preceding claims, characterized in that the radial-sealing-segment control channel ( 65 ) as a chamfer ( 65.1 . 65.2 . 65.5 . 65.6 ) or as a groove ( 65.3 . 65.4 ) is designed. Motor-pump unit according to one of Claims 2 to 12, characterized in that the radial-sealing-segment control channel ( 65 ) between the segment spring groove ( 51.1 . 51.2 ) and the sealing roller groove ( 48.1 . 48.2 ). Motor-pump unit according to one of claims 2 to 13, characterized in that the radial sealing segment control channel ( 65 ) into the segment spring groove ( 51.1 . 52.2 ) and / or in the sealing roller groove ( 48.1 . 48.2 ) opens. Motor-pump unit according to one of claims 2 to 14, characterized in that the radial sealing segment control channel ( 65 ) between the segment spring groove ( 51.1 . 51.2 ) and the stop surface ( 55.1 . 55.2 ) of the stop ( 54.1 . 54.2 ). Motor-pump unit according to one of claims 2 to 15, characterized in that the radial sealing segment control channel ( 65 ) up to the stop surface ( 55.1 . 55.2 ) of the stop ( 54.1 . 54.2 ). Motor-pump unit according to one of claims 2 to 16, characterized in that the radial sealing segment control channel ( 65 ) beyond the stop surface ( 55.1 . 55.2 ) of the stop ( 54.1 . 54.2 ) up to a ring gear teeth of the ring gear teeth ( 31 ) of the ring gear ( 30 ) opposite open space ( 67.1 . 67.2 ) of the pinion segment ( 42 ) or the ring gear segment extends. Motor-pump unit according to one of the preceding claims, characterized in that the Radialdichtsegmente a single pinion segment ( 42 ) and at least two or exactly two ring gear segments ( 43.1 . 43.2 ) and / or that the radial sealing segments a single ring gear segment ( 42 ) and at least two or exactly two pinion segments ( 43.1 . 43.2 ). Motor-pump unit according to one of the preceding claims, characterized in that the pinion segment ( 42 ) and / or the ring gear segment ( 43.1 . 43.2 ) by means of at least one retaining pin ( 45.1 . 45.2 ), which in one of the axial end faces ( 56.1 . 57.1 ; 56.2 . 57.2 ) of the gears ( 26 . 30 ) opposite housing part ( 25.1 . 25.2 ) of Housing ( 25 ) is rotatably mounted, against a displacement in the direction of a low-pressure region of the working chamber ( 24 ), wherein the retaining pin ( 45.1 . 45.2 ) at its the filler ( 41 ) associated with a holding body ( 86.1 . 86.2 ), which, in a cross-section perpendicular to the axial direction ( 39 ), has a V-shaped or trapezoidal cross-section and holding body support surfaces ( 71.1 . 71.2 ) which forms an acute angle ( 70 ) and wherein the pinion segment ( 42 ) and / or the ring gear segment at least one sealing segment recess ( 80.1 . 80.2 ) for receiving the holding body ( 86.1 . 86.2 ) of the at least one retaining pin ( 45.1 . 45.2 ), which, in a cross-section perpendicular to the axial direction ( 39 ), also has a V-shaped or a trapezoidal cross section and sealing segment support surfaces ( 71.3 . 71.4 ), which also has an acute angle ( 70.1 ), and wherein both the support body support surfaces ( 71.1 . 71.2 ) as well as the sealing segment support surfaces ( 71.3 . 71.4 ) wedge-shaped towards a center to the pinion ( 26 ), and wherein the at least one retaining pin ( 45.1 . 45.2 ) with its holding body ( 86.1 . 86.2 ) in the at least one sealing segment recess ( 80.1 . 80.2 ) intervenes. Motor-pump unit according to claim 19, characterized in that the respective angle ( 70 . 70.1 ) Is 20 degrees to 30 degrees or 24 degrees. Motor-pump unit according to one of the preceding claims, characterized in that the filling piece ( 41 ) and / or the at least one axial sealing plate ( 58.1 . 58.2 ) symmetrical to an imaginary the pinion rotation axis ( 34.2 ) and the ring gear rotation axis ( 36 ) containing symmetry plane ( 87 ) is designed or are.

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